US9188107B2 - Wind turbine bearings - Google Patents

Wind turbine bearings Download PDF

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Publication number
US9188107B2
US9188107B2 US14/014,695 US201314014695A US9188107B2 US 9188107 B2 US9188107 B2 US 9188107B2 US 201314014695 A US201314014695 A US 201314014695A US 9188107 B2 US9188107 B2 US 9188107B2
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Prior art keywords
raceway
roller elements
pitch bearing
race
wall
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US14/014,695
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US20150063736A1 (en
Inventor
Adam Daniel Minadeo
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GE Infrastructure Technology LLC
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General Electric Co
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Assigned to GENERAL ELECTRIC COMPANY reassignment GENERAL ELECTRIC COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MINADEO, ADAM DANIEL
Priority to DKPA201470512A priority patent/DK179076B1/en
Priority to DE102014112473.1A priority patent/DE102014112473A1/de
Publication of US20150063736A1 publication Critical patent/US20150063736A1/en
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Publication of US9188107B2 publication Critical patent/US9188107B2/en
Assigned to GE INFRASTRUCTURE TECHNOLOGY LLC reassignment GE INFRASTRUCTURE TECHNOLOGY LLC ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GENERAL ELECTRIC COMPANY
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Classifications

    • F03D11/0008—
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D7/00—Controlling wind motors 
    • F03D7/02—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor
    • F03D7/022—Adjusting aerodynamic properties of the blades
    • F03D7/0224—Adjusting blade pitch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/70—Bearing or lubricating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/08—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with two or more rows of balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/185—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with two raceways provided integrally on a part other than a race ring, e.g. a shaft or housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/581—Raceways; Race rings integral with other parts, e.g. with housings or machine elements such as shafts or gear wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/70—Adjusting of angle of incidence or attack of rotating blades
    • F05B2260/79—Bearing, support or actuation arrangements therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/30—Angles, e.g. inclinations
    • F16C2240/34—Contact angles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the present subject matter relates generally to wind turbines and, more particularly, to improved bearing configurations for a wind turbine.
  • Wind power is considered one of the cleanest, most environmentally friendly energy sources presently available, and wind turbines have gained increased attention in this regard.
  • a modern wind turbine typically includes a tower, generator, gearbox, nacelle, and one or more rotor blades.
  • the rotor blades capture kinetic energy from wind using known airfoil principles and transmit the kinetic energy through rotational energy to turn a shaft coupling the rotor blades to a gearbox, or if a gearbox is not used, directly to the generator.
  • the generator then converts the mechanical energy to electrical energy that may be deployed to a utility grid.
  • the loads acting on a rotor blade are transmitted through the blade and into the blade root. Thereafter, the loads are transmitted through a pitch bearing disposed at the interface between the rotor blade and the wind turbine hub.
  • pitch bearings typically include two rows of balls concentrically disposed within separate raceways defined between inner and outer races, with each ball being configured to contact its corresponding raceway at four separate contact points. Under ideal loading conditions, the loads transmitted through the pitch bearing are distributed evenly over all of the balls. However, due to dynamic loading on the pitch bearing and the difference in stiffness between the hub and the rotor blade, only a small percentage of the balls actually end-up carrying the loads during operation of the wind turbine.
  • the present subject matter is directed to a pitch bearing for coupling a rotor blade to a hub of a wind turbine.
  • the pitch bearing may generally include an outer race configured to be coupled to the hub.
  • the outer race may define a first outer raceway wall.
  • the first outer raceway wall may define a curved profile having a center of curvature.
  • the pitch bearing may also include an inner race rotatable relative to the outer race and configured to be coupled to the rotor blade.
  • the inner race may define a first inner raceway wall.
  • the first inner raceway wall may define a curved profile having a center of curvature.
  • the pitch bearing may include a plurality of roller elements disposed between the first inner and outer raceway walls. Each of the roller elements may define a geometric center. The center of curvature for each of the first inner raceway wall and the first outer raceway wall may be offset from the geometric center of each of the first plurality of roller elements.
  • the present subject matter is directed to a pitch bearing for coupling a rotor blade to a hub of a wind turbine.
  • the pitch bearing may include an outer race configured to be coupled to the hub.
  • the outer race may define a first outer raceway wall and a second outer raceway wall.
  • the pitch bearing may also include an inner race rotatable relative to the outer race and configured to be coupled to the rotor blade.
  • the inner race may define a first inner raceway wall and a second inner raceway wall.
  • the inner race may be at least partially spaced apart from the outer race such that a first gap is defined between the inner and outer races along an upper portion of the pitch bearing and a second gap is defined between the inner and outer races along a lower portion of the pitch bearing.
  • the pitch bearing further includes a first plurality of roller elements disposed between the first inner and outer raceway walls and a second plurality of roller elements disposed between the second inner and outer raceway walls. Additionally, the pitch bearing includes a first seal disposed within the first gap directly between the inner and outer races and a second seal disposed within the second gap directly between the inner and outer races. The pitch bearing also includes a lubrication port defined through the outer race. The lubrication port may be configured to supply a lubricant from a location outside the pitch bearing to a location between the first and second plurality of roller elements.
  • the present subject matter is directed to a slewring bearing for a wind turbine.
  • the slewring bearing may include an outer race and an inner race rotatably coupled to the outer race.
  • the inner race may be positioned relative to the outer race such that a raceway is defined between the inner and outer races.
  • the slewring bearing may include a plurality of roller elements extending circumferentially around the raceway such that a single contact point is defined directly between each pair of adjacent roller elements.
  • FIG. 1 illustrates a perspective view of one embodiment of a wind turbine
  • FIG. 2 illustrates a perspective, internal view of the nacelle of the wind turbine shown in FIG. 1
  • FIG. 3 illustrates a perspective view of one of the rotor blades of the wind turbine shown in FIG. 1 ;
  • FIG. 4 illustrates a cross-sectional view of one embodiment of a rotor blade coupled to a wind turbine hub via a pitch bearing configured in accordance with aspects of the present subject matter
  • FIG. 5 illustrates a cross-sectional view of a portion of the pitch bearing shown in FIG. 4 ;
  • FIG. 6 illustrates a close-up, cross-sectional view of a portion of the pitch bearing shown in FIG. 5 ;
  • FIG. 7 illustrates another cross-sectional view of the pitch bearing shown in FIG. 5 , particularly illustrating the force span resulting from the disclosed bearing configuration
  • FIG. 8 illustrates a cross-sectional view of another embodiment of a pitch bearing configured in accordance with aspects of the present subject matter
  • FIG. 9 illustrates a perspective view of the pitch bearing shown in FIG. 4 ;
  • FIG. 10 illustrates a perspective, partially cut-away view of another embodiment of a pitch bearing, particularly illustrating the pitch bearing including a full complement of roller elements around each row of roller elements;
  • FIG. 11 illustrates a close-up view of a portion of the pitch bearing shown in FIG. 10 .
  • a pitch bearing of the wind turbine may include a first raceway and a second raceway defined between inner and outer races of the bearing.
  • the raceways may be configured such that the roller elements of the bearing contact the raceways at two opposed contact points oriented at a contact angle relative to the radial and axial directions.
  • the disclosed bearing configuration(s) may allow for lower resultant loads to be applied through the roller elements, thereby reducing localized stress and decreasing the likelihood of component damage/failure.
  • the pitch bearing may also include a raceway rib at least partially separating the first and second raceways.
  • the raceway rib may be configured to extend beyond a 90 degree location of each roller element. As a result, the roller elements may be prevented from running up and over the edge(s) of the raceways during dynamic loading conditions.
  • the disclosed pitch bearings have been uniquely configured to handle the dynamic loading of a wind turbine. Specifically, due to erratic moment loading and the fact that each pitch bearing is mounted directly to a relatively flexible rotor blade, pitch bearings must be equipped to handle axial and radial loads that can vary significantly with time. As will be described below, the disclosed bearings provide for higher contact angles and a wider support base (i.e., wider load span), thereby reducing the resultant loads applied through each roller element. Accordingly, each roller element may deflect less and, thus, may retain more of an overall share of the entire load, thereby decreasing the stress on the bearing.
  • the disclosed bearing configurations may be utilized within any suitable wind turbine bearing.
  • yaw bearings are often subject to dynamic loading during operation of a wind turbine.
  • the disclosed bearing configurations may also be implemented within the yaw bearing of a wind turbine to reduce stresses within the bearing.
  • FIG. 1 illustrates a side view of one embodiment of a wind turbine 10 .
  • the wind turbine 10 generally includes a tower 12 , a nacelle 14 mounted on the tower 12 , and a rotor 16 coupled to the nacelle 14 .
  • the rotor 16 includes a rotatable hub 18 and at least one rotor blade 20 coupled to and extending outwardly from the hub 18 .
  • the rotor 16 includes three rotor blades 20 .
  • the rotor 16 may include more or less than three rotor blades 20 .
  • Each rotor blade 20 may be spaced about the hub 18 to facilitate rotating the rotor 16 to enable kinetic energy to be transferred from the wind into usable mechanical energy, and subsequently, electrical energy.
  • the hub 18 may be rotatably coupled to an electric generator 224 ( FIG. 2 ) positioned within the nacelle 14 to permit electrical energy to be produced.
  • a generator 224 may be disposed within the nacelle 16 .
  • the generator 224 may be coupled to the rotor 16 of the wind turbine 10 for generating electrical power from the rotational energy generated by the rotor 16 .
  • the rotor 16 may include a rotor shaft 226 coupled to the hub 18 for rotation therewith.
  • the generator 224 may then be coupled to the rotor shaft 226 such that rotation of the rotor shaft 226 drives the generator 224 .
  • the generator 224 includes a generator shaft 228 rotatably coupled to the rotor shaft 226 through a gearbox 230 .
  • the generator shaft 228 may be rotatably coupled directly to the rotor shaft 226 .
  • the generator 224 may be directly rotatably coupled to the rotor shaft 226 (often referred to as a “direct-drive wind turbine”).
  • the wind turbine 10 may include one or more yaw drive mechanisms 232 mounted to and/or through a bedplate 234 positioned atop the wind turbine tower 12 .
  • each yaw drive mechanism 232 may be mounted to and/or through the bedplate 234 so as to engage a yaw bearing 236 coupled between the bedplate 234 and the tower 12 of the wind turbine 10 .
  • the yaw bearing 236 may be mounted to the bed plate 234 such that, as the yaw bearing 236 rotates about a yaw axis (not shown) of the wind turbine 10 , the bedplate 234 and, thus, the nacelle 14 are similarly rotated about the yaw axis.
  • each yaw drive mechanism 232 may have any suitable configuration and may include any suitable components known in the art that allow such mechanisms 232 to function as described herein.
  • each yaw drive mechanism 232 may include a yaw motor 244 mounted to the bedplate 234 .
  • the yaw motor 244 may be coupled to a yaw gear 246 (e.g., a pinion gear) configured to engage the yaw bearing 236 .
  • the yaw motor 244 may be coupled to the yaw gear 246 directly (e.g., by an output shaft (not shown) extending through the bedplate 234 ) or indirectly through a suitable gear assembly coupled between the yaw motor 244 and the yaw gear 246 .
  • the torque generated by the yaw motor 244 may be transmitted through the yaw gear 246 and applied to the yaw bearing 236 to permit the nacelle 14 to be rotated about the yaw axis of the wind turbine 10 .
  • the illustrated wind turbine 10 is shown as including two yaw drive mechanisms 232 , the wind turbine 10 may generally include any suitable number of yaw drive mechanisms 232 .
  • the yaw bearing 236 may generally have any suitable configuration, including one or more of the bearing configurations described below.
  • the yaw bearing 236 may include an inner race and an outer race rotatable relative to the inner race, with one or more rows of roller elements being disposed between the inner and outer races.
  • the yaw gear 246 may be configured to engage the outer race of the yaw bearing 236 such that the outer race is rotated relative to the inner race to adjust the orientation of the nacelle 14 relative to the direction of the wind.
  • the wind turbine 10 may also include a plurality of pitch bearings 50 , with each pitch bearing 50 being coupled between the hub 18 and one of the rotor blades 20 .
  • the pitch bearings 50 may be configured to allow each rotor blade 20 to be rotated about its pitch axis 252 (e.g., via a pitch adjustment mechanism 72 ), thereby allowing the orientation of each blade 20 to be adjusted relative to the direction of the wind.
  • the term “slewring bearing” may be used to refer to the yaw bearing 236 of the wind turbine 10 and/or one of the pitch bearings 50 of the wind turbine 10 .
  • the rotor blade 20 includes a blade root 22 configured for mounting the rotor blade 20 to the hub 18 of a wind turbine 10 ( FIG. 1 ) and a blade tip 24 disposed opposite the blade root 22 .
  • a body 26 of the rotor blade 20 may extend lengthwise between the blade root 22 and the blade tip 24 and may generally serve as the outer shell of the rotor blade 20 .
  • the body 26 may define an aerodynamic profile (e.g., by defining an airfoil shaped cross-section, such as a symmetrical or cambered airfoil-shaped cross-section) to enable the rotor blade 20 to capture kinetic energy from the wind using known aerodynamic principles.
  • the body 26 may generally include a pressure side 28 and a suction side 30 extending between a leading edge 32 and a trailing edge 34 .
  • the rotor blade 20 may have a span 36 defining the total length of the body 26 between the blade root 22 and the blade tip 24 and a chord 38 defining the total length of the body 26 between the leading edge 32 and the trailing edge 34 .
  • the chord 38 may vary in length with respect to the span 26 as the body 26 extends from the blade root 22 to the blade tip 24 .
  • each root attachment assembly 40 may include a barrel nut 42 mounted within a portion of the blade root 22 and a root bolt 44 coupled to and extending from the barrel nut 42 so as to project outwardly from a root end 46 of the blade root 22 .
  • the root bolts 44 may generally be used to couple the blade root 22 to the hub 18 (e.g., via one of the pitch bearings 50 ), as will be described in greater detail below.
  • the pitch bearing 50 includes an outer bearing race 52 , an inner bearing race 54 , and a plurality of roller elements 56 , 58 (e.g., a first row of balls 56 and a second row of balls 58 ) disposed between the outer and inner races 52 , 54 .
  • the outer race 52 may generally be configured to be mounted to a hub flange 60 of the hub 18 using a plurality of hub bolts 62 and/or other suitable fastening mechanisms.
  • each root bolt 44 may extend between a first end 64 and a second end 66 .
  • the first end 64 may be configured to be coupled to a portion of the inner race 54 , such as by coupling the first end 64 to the inner race 54 using an attachment nut and/or other suitable fastening mechanism.
  • the second end 66 of each root bolt 44 may be configured to be coupled to the blade root 22 via the barrel nut 42 of each root attachment assembly 40 .
  • the inner race 54 may be configured to be rotated relative to the outer race 52 (via the roller elements 56 , 58 ) to allow the pitch angle of each rotor blade 20 to be adjusted. As shown in FIG. 4 , such relative rotation of the outer and inner races 52 , 54 may be achieved using a pitch adjustment mechanism 72 mounted within a portion of the hub 18 .
  • the pitch adjustment mechanism 72 may include any suitable components and may have any suitable configuration that allows the mechanism 72 to function as described herein.
  • the pitch adjustment mechanism 72 may include a pitch drive motor 74 (e.g., an electric motor), a pitch drive gearbox 76 , and a pitch drive pinion 78 .
  • the pitch drive motor 74 may be coupled to the pitch drive gearbox 76 so that the motor 74 imparts mechanical force to the gearbox 76 .
  • the gearbox 76 may be coupled to the pitch drive pinion 78 for rotation therewith.
  • the pinion 78 may, in turn, be in rotational engagement with the inner race 54 .
  • a plurality of gear teeth 80 may be formed along the inner circumference of the inner race 54 , with the gear teeth 80 being configured to mesh with corresponding gear teeth 82 formed on the pinion 78 .
  • rotation of the pitch drive pinion 78 results in rotation of the inner race 54 relative to the outer race 52 and, thus, rotation of the rotor blade 20 relative to the hub 18 .
  • each raceway 110 , 112 may be defined by separate walls of the outer and inner races 52 , 54 .
  • FIGS. 5 and 6 close-up, cross-sectional views of portions of the pitch bearing 50 shown in FIG. 4 are illustrated in accordance with aspects of the present subject matter.
  • the roller elements 56 , 58 are configured to be received within separate raceways defined between the inner and outer races 52 , 54 .
  • a first raceway 110 is defined between the inner and outer races 52 , 54 for receiving the first row of roller elements 56
  • a second raceway 112 is defined between the inner and outer races 52 , 54 for receiving the second row of roller elements 58 .
  • each raceway 110 , 112 may be defined by separate walls of the outer and inner races 52 , 54 .
  • the first raceway 110 is defined by a first outer raceway wall 114 of the outer race 52 and a first inner raceway wall 116 of the inner race 54 .
  • the second raceway 112 is defined by a second outer raceway wall 118 of the outer race 54 and a second inner raceway wall 120 of the inner race 120 .
  • each raceway wall 114 , 116 , 118 , 120 may be configured to define a curved profile.
  • the first outer raceway wall 114 generally corresponds to a curved wall extending around the inner circumference of the outer race 52 that defines a radius 122 extending from a center of curvature 124 of such wall.
  • the first inner raceway wall 114 generally corresponds to a curved wall extending around the outer circumference of the inner race 54 that defines a radius 126 extending from a center of curvature 128 of such wall.
  • the second outer raceway wall 118 may also define a radius having a center of curvature and the second inner raceway wall 120 may similarly define a radius having a center of curvature.
  • the center of curvature 124 , 128 for each raceway wall 114 , 116 , 118 , 120 may be offset from a geometric center 130 of each roller element 56 , 58 .
  • the center of curvature 124 of the first outer raceway wall 114 is offset from the geometric center 130 of the roller element 56 by a first distance 132 while the center of curvature 128 of the first inner raceway wall 116 is offset from the geometric center 130 by a second distance 134 .
  • the second outer and inner raceway walls 118 , 120 may be configured similar to the first outer and inner raceway walls 114 , 116 .
  • the centers of curvature for the second outer and inner raceway walls 118 , 120 may be offset from the geometric center 130 of each roller element 58 by respective distances (e.g., the first and second distances 132 , 134 ).
  • the first distance 132 may be the same as the second distance 134 .
  • the first distance 132 may differ from the second distance 134 .
  • the distances 132 , 134 may generally correspond to any suitable length.
  • the first and second distances 132 , 134 may each correspond to a length ranging from about 0.1 millimeters (mm) to about 5 mm, such as from about 0.4 mm to about 1 mm or from about 1.3 mm to about 2.5 mm and any other subranges therebetween.
  • each roller element 56 , 58 may include two contact points 136 , 138 , 140 , 142 defined along reference lines 144 that are angled relative to the radial direction (indicated by arrow 146 ) and the axial direction (indicated by arrow 148 ) of the pitch bearing 50 .
  • each roller element 56 is configured to contact the first outer raceway wall 114 at a first outer contact point 136 and the first inner raceway wall 116 at a first inner contact point 138 , with the first outer and inner contact points 136 , 138 being defined along a reference line 144 oriented at a first contact angle 150 .
  • each roller element 58 may be configured to contact the second outer raceway wall 118 at a second outer contact point 140 and the second inner raceway wall 120 at a second inner contact point 142 , with the second outer and inner contact points 140 , 142 being defined along a reference line 144 oriented at a second contact angle 152 .
  • each reference line 144 may be configured to extend at a contact angle 150 , 152 relative to the radial direction 146 ranging from about 15 degrees to about 85 degrees, such as from about 40 degrees to about 48 degrees or from about 49 degrees to about 70 degrees and any other subranges therebetween.
  • first and second contact angles 150 , 152 may be the same angle or different angles. Specifically, as the contact angle approaches zero degrees, the corresponding roller elements may be better equipped to handle radial loads whereas, as the contact angle approaches ninety degrees, the corresponding roller elements may be better equipped to handle axial loads.
  • each row of roller elements 56 , 58 may be stiffer in a given direction, such as by configuring the first row of roller elements 56 to be axially stiffer (e.g., by selecting the first contact angle 150 to be closer to 90 degrees) and the second row of roller elements 58 to be radially stiffer (e.g., by selecting the second contact angle 152 to be closer to 0 degrees).
  • the roller elements 56 , 58 may be capable of carrying both radial and axial loads.
  • the contact points 136 , 138 , 140 , 142 so that the reference lines 144 intersect one another (as opposed to being parallel), an increased force span may be defined at the center of the pitch bearing 50 , thereby resulting in lower resultant forces being applied through the roller elements 56 , 58 . For example, as shown in FIG.
  • the reference lines 144 are angled away from each other so that a large force span 154 is defined along a center line 156 extending through the center of the pitch bearing 50 .
  • the force on the roller elements 56 , 58 resulting from moment loading 158 on the pitch bearing 50 is generally equal to the moment divided by the force span 154 .
  • the resultant forces transmitted through the roller elements 56 , 58 may be reduced, thereby decreasing the risk of damage to and/or failure of the pitch bearing components.
  • the pitch bearing may also include a raceway rib 160 at least partially dividing the first raceway 110 from the second raceway 112 .
  • the raceway rib 160 may form an extension of the outer race 52 .
  • the raceway rib 160 may correspond to a radial projection of the outer race 52 that extends between the roller elements 56 , 58 and separates the first outer raceway wall 114 from the second outer raceway wall 118 .
  • the raceway rib 160 may be configured to form an extension of the inner race 54 .
  • the raceway rib 160 may correspond to a radial projection of the inner race 54 configured to extend between the roller elements 56 , 58 and separate the first inner raceway wall 116 from the second inner raceway wall 118 .
  • the raceway rib 160 may be configured such that the raceway walls defining the outer surfaces of the rib 160 extend beyond a 90 degree location of the roller elements 56 , 58 , which is indicated by a reference line 162 passing through the geometric center 130 of the roller elements 56 , 58 and extending along the axial direction 148 (i.e., perpendicular to the radial direction 146 ).
  • the raceway rib 160 extends between the roller elements 56 , 58 such that the arc length of the portion of the outer raceway walls 114 , 118 extending beyond the 90 degree location 162 defines an angle 164 ranging from about 0 degrees to about 60 degrees, such as from about 15 degrees to about 45 degrees or from about 25 degrees to about 50 degrees and any other subranges therebetween.
  • the raceway rib 160 is configured as an extension of the inner race 150
  • the inner raceway walls 116 , 120 may also be configured to extend beyond the 90 degree location 162 at such an angle 164 .
  • the roller elements 56 , 58 may be fully supported within the pitch bearing 50 during dynamic loading events. For instance, if the roller elements 56 , 58 run up/down the raceway walls 114 , 116 , 118 , 120 towards the 90 degree location 162 during high loading events, the roller elements 56 , 58 may be supported between the inner and outer races 52 , 54 without contacting the edges of the raceways 110 , 112 (e.g., edges 166 ( FIG. 6 ) defined by the outer raceway walls 114 , 118 ).
  • a plurality of lubrication ports 168 may be defined through the outer race 52 .
  • the lubrication ports 168 may be spaced apart circumferentially around the outer circumference of the outer race 52 .
  • each lubrication port 168 may be configured to supply a suitable lubricant (e.g., grease, etc.) from a location outside the pitch bearing 50 to a location between the first and second raceways 110 , 112 .
  • a suitable lubricant e.g., grease, etc.
  • each lubrication port 168 may generally extend between a first end 170 disposed along the outer circumference of the outer race 52 and a second end 172 disposed along the inner circumference of the outer race 52 .
  • the second end 172 is defined through the raceway rib 160 so that lubricant may be delivered into the gap defined between the rib 160 and the outer circumference of the inner race 54 .
  • the lubricant may then be directed up and down between the outer and inner races 52 , 54 to lubricate the first and second raceways 110 , 112 .
  • any gaps defined between the outer and inner races 52 , 54 may be sealed using suitable sealing mechanisms.
  • the pitch bearing includes a first gap 174 defined between the outer and inner races 52 , 54 along an upper portion 176 of the bearing 50 and a second gap 178 defined between the outer and inner races 52 , 54 along a lower portion 180 of the bearing 50 .
  • a first sealing mechanism 182 may be disposed directly between the outer inner races 52 , 54 to seal the first gap 174
  • a second sealing mechanism 184 may be disposed directly between the outer and inner races 52 , 54 to seal the second gap 178 .
  • roller elements 56 , 58 contained within each row may be spaced apart circumferentially from one another using conventional cages and/or spacers.
  • the pitch bearing 50 may include a full complement of roller elements 56 , 58 extending circumferentially around each raceway 110 , 112 .
  • bearing configuration(s) shown in FIGS. 4-9 may be utilized with any other suitable wind turbine bearing(s).
  • the bearing configuration(s) may be utilized within the yaw bearing 236 of a wind turbine 10 .
  • FIGS. 10 and 11 perspective views of another embodiment of a bearing configuration are illustrated in accordance with aspects of the present subject matter.
  • FIG. 10 illustrates a perspective, partially cut-away view of a pitch bearing 50 having a full complement of roller elements 56 , 58 .
  • FIG. 11 illustrates a close-up view of a portion of the pitch bearing 50 shown in FIG. 10 .
  • the pitch bearing 50 may include a plurality of roller elements 56 , 58 (i.e., balls) extending circumferentially around each raceway 110 , 112 , with each roller element 56 , 58 directly contacting its adjacent roller elements 56 , 58 .
  • the roller elements 56 , 58 may be installed within each raceway 110 , 112 such that a single contact point 190 is defined between each pair of adjacent roller elements 56 , 58 .
  • additional roller elements may be installed within the bearing 50 .
  • conventional bearing configurations typically include separators, such as cages and/or spacers, that are designed to space the roller elements 56 , 58 apart circumferentially around each raceway 110 , 112 .
  • separators such as cages and/or spacers
  • the space typically inhabited by such separators may be replaced with additional roller elements 56 , 58 .
  • the load capacity of the bearing 50 may be increased while the stresses acting on the bearing 50 may be reduced.
  • the full complement of roller elements 56 , 58 shown in FIGS. 10 and 11 may be utilized together with the bearing configuration described above with reference to FIGS. 4-9 .
  • the full complement of roller elements 56 , 58 may be utilized together with any other suitable pitch bearing configuration, including conventional pitch bearing configurations.
  • the bearing configuration shown in FIGS. 10 and 11 may be utilized with any other suitable wind turbine bearing(s).
  • the full complement of roller elements 56 , 58 may be utilized within the yaw bearing 236 of a wind turbine 10 .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rolling Contact Bearings (AREA)
  • Wind Motors (AREA)
US14/014,695 2013-08-30 2013-08-30 Wind turbine bearings Active 2033-09-18 US9188107B2 (en)

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DE102014112473.1A DE102014112473A1 (de) 2013-08-30 2014-08-29 Lager für Windkraftanlage

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Cited By (6)

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US20120020792A1 (en) * 2009-01-14 2012-01-26 Hubertus Frank Wind power plant
US20150098669A1 (en) * 2013-09-27 2015-04-09 Aktiebolaget Skf Rotative Assembly, Method For Dismounting A Sealing Element And Extraction Tool For Dismounting A Sealing Element
US20190219036A1 (en) * 2018-01-18 2019-07-18 Siemens Gamesa Renewable Energy A/S Bearing arrangement and a wind turbine
US20220341465A1 (en) * 2019-09-24 2022-10-27 Segos Co., Ltd. Bearing assembly
US11668342B2 (en) 2019-02-01 2023-06-06 Roller Bearing Company Of America, Inc. Integrated stud ball bearing with precision matched raceway contact angles for consistent stiffness of gimbal assembly
US11725633B2 (en) * 2017-03-28 2023-08-15 General Electric Company Pitch bearing for a wind turbine

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DE102013215962A1 (de) * 2013-08-13 2015-03-12 Schaeffler Technologies AG & Co. KG Rundtischlager
DE102015207476A1 (de) * 2015-04-23 2016-10-27 Aktiebolaget Skf Mehrreihiges Wälzlager und Windkraftanlage mit zumindest einem mehrreihigen Wälzlager
CN104895726B (zh) * 2015-07-02 2017-10-27 国电联合动力技术有限公司 一种潮汐能发电机组及其变桨轴承
DE102015009865B4 (de) * 2015-08-04 2022-09-29 Imo Holding Gmbh Drehverbindung
US10677290B2 (en) * 2017-10-13 2020-06-09 General Electric Company Wind turbine pitch bearing with line contact rolling elements
EP3788260A4 (de) * 2018-05-03 2021-11-24 General Electric Company Pitchlager für eine windturbine
CN111255631A (zh) * 2020-02-15 2020-06-09 吴志华 一种风力发电机变桨装置
DE102020133940A1 (de) * 2020-12-17 2022-06-23 Renk Gmbh Gleitlager mit Gleitsegmenten

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120020792A1 (en) * 2009-01-14 2012-01-26 Hubertus Frank Wind power plant
US9739263B2 (en) * 2009-01-14 2017-08-22 Imo Holding Gmbh Wind power plant
US20150098669A1 (en) * 2013-09-27 2015-04-09 Aktiebolaget Skf Rotative Assembly, Method For Dismounting A Sealing Element And Extraction Tool For Dismounting A Sealing Element
US9541136B2 (en) * 2013-09-27 2017-01-10 Aktiebolaget Skf Rotative assembly, method for dismounting a sealing element and extraction tool for dismounting a sealing element
US11725633B2 (en) * 2017-03-28 2023-08-15 General Electric Company Pitch bearing for a wind turbine
US20190219036A1 (en) * 2018-01-18 2019-07-18 Siemens Gamesa Renewable Energy A/S Bearing arrangement and a wind turbine
US10989174B2 (en) * 2018-01-18 2021-04-27 Siemens Gamesa Renewable Energy A/S Bearing arrangement and a wind turbine
US11668342B2 (en) 2019-02-01 2023-06-06 Roller Bearing Company Of America, Inc. Integrated stud ball bearing with precision matched raceway contact angles for consistent stiffness of gimbal assembly
US20220341465A1 (en) * 2019-09-24 2022-10-27 Segos Co., Ltd. Bearing assembly

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DK179076B1 (en) 2017-10-09

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